Control device



June 6, 1939. F. s. DENISON ET AL CONTROL DEV ICE Filed Dec. 20, 1934 2 Sheets-Sheet l gmnmtoz w .my i mm 5 Sr K .NG ea C F June 6, 1939. F. s. DENISON ET AL CONTROL DEVICE Filed Dec. 20, 1934 2 Sheets-Sheet 2 gwuwntoz Frederick SDeni-son Carl, G. Kranmiller Patented June 6, 1939 UNITED, STATES PATENT OFFICE CONTROL DEVICE Frederick S. Denison and Carl G.

Minneapolis,

Kronmiller,

Minn assignors to Minneapolis- Honeywell Regulator Company, 'Min'n., a corporation of Delaware Minneapolis,

Application December 20, i934, Serial No. 758,416

' 10 Claims.

10 gas under the control of one or more control.

valves that may be automatically or manually operated, or both. Features of the invention reside in the control of the pressure motor as well as the manner in which the pressure motor, or

15 for that matter any motor, controls a plurality of devices.

An object of the present invention is the provision of an improved control system for controlling pressure motors.

20 Another object of the invention is the provision of a control arrangement in which a single motor operates a fuel valve, an air damper and a pilot valve.

A further object of the invention is the pro- 25 vision of a mechanism by which a single motor first operates a pilot valve, or an air damper, or

both, and then operates a fuel valve, whereby the pilot is opened or expanded or the air damper is opened or partly opened, or both of these func- 30 tions take place, prior to opening of the fuel valve.

Other objects of the invention include the detailed manner in which the above results are obtained and include such details in combination with the improved pressure motor control system. 35 Further objects will'be found in the drawings,

detailed description and appended claims. For a more complete understanding of the invention, reference may be had to the following detailed description and accompanying drawings,

L in which:

Fig. 1 is a sectional view of one modification of the present invention,

Fig 2 is a detail of certain parts of the pressure motor shown in Fig. 1,

Fig. 3 is a showing of theapparatus of Fig. 1 as applied to a gas-fired heater and controlled by a conventional room thermostat, and

Fig. 4 is a sectional view of a modified form of the invention.

0 Referring first to Figs. 1 and 2, the apparatus of the present invention includes a motor means,v generally indicated at I3, which is herein shown 1 in the form of a pressure motor although it willbecome apparent as this description proceeds that i many'of the features of the present invention are applicable to motors of other types; The pressure motor I0 comprises a lower casting ii, an upper casting, l2, and a diaphragm I3 which is sealed between the lower and upper castings II and I2. The lower casting H and the diaphragm l3 form 5 a pressure chamber l4 of which the diaphragm l3 constitutes a movable wall. Similarly, the upper casting l2 and diaphragm l3 form a sealed chamber l5 of which the diaphragm l3 likewise constitutes a movable wall. The diaphragm I3 is adapted to control the flow of fluid through a valve having a casing l6 that is provided with the usual inlet I1 and outlet I 8. This valve casing I6 is secured to the lower casting I I by an assembly which comprises a bracket is, a collar 20 and a circular disc 2|, The collar is provided with a flange 22 which overlies the circular disc 2| and the circular disc 2| is secured to the bracket is by any suitable means such as the rivets 23. The bracket I9 is secured to the lower 20 casting II as by screws 24 and this lower casting I I is provided with an opening 25 so that pressure chamber l4 communicates with the interior of bracket IS. The valve casing I6 is provided with an upwardly extending cylindrical extension 26 25 that is exteriorly screw-threaded so that the collar 20 can be screw-threaded thereon and thereby firmly clamps the end of cylindrical extension 26 against the circular disc 2| in fluid-tight relation.

The valve casing I6 is provided with the usual 30 partition wall 30, having an opening 3| therein, 3 to thereby form a valve seat 32. A valve disc 33 cooperates with the valve seat 32 and is carried by a valve stem 34. The valve 'stem 34 extends upwardlythrough a guide or bushing 35 that is 35 fixed to the bracket I9 and extends downwardly through the circular disc 2|. The valve stem 34 further extends upwardly into and terminates within the pressure chamber l4.

Counter-weights and 4| are located on the 40 upper and lower sides of diaphragm l3 substan- T tially at the center thereof and are secured there'- to by suitable means such as rivets 42. A bracket 43 is also secured to the lower side of diaphragm l3 and preferably by means of these same rivets I 42 which secure the counter-weights 40 and 4| thereto. The valve stem 34 extends through the bracket 43 and is provided with a pin 44 extending therethrough so that upward movement of bracket 43 first results in taking up the lost motion between the bracket 43 and pin 44 and thereafter the bracket 43 engages the pin 44 to lift valve disc 33 from engagement with valve seat 32. A washer 45 is preferably interposed between the upper surface'of bracket 43 and the pin 44. Valve stem 34 also passes through a counter-weight. The downward movement of counter-weight 46 on valve stem 34 is limited as by means of a pin 41.

From: the foregoing, it will be apparent that the valve disc 33 is normally biased towards closed position by the counter-weight 46 and the diaphragm I3 is normally biased to its lower position, in which it is shown, by means of counter-weights 48 and 4| pressures in pressure chamber I4 and sealing chamber, I are equal, the diaphragm I3 and the valve disc 33 aremoved to the position shown-in Fig. 1. However, if the pressure in pressure chamber. I4 is made substantially greater than the pressure in sealing chamber I5, then the diaphragm l3 will move upwardly. Initial upward movement serves to take up the lost motion between washer 45 and pin 44. Thereafter, the valve stem 34 is raised to lift valve disc 33 from. engagement with the valve seat 32. Then if the pressures in pressure chamber I4 and sealing chamber I5 are again equalized, the diaphragm l3 will move downwardly, allowing valve disc 33 to seat upon valve seat 32 after which the diaphragm I3 will continue its downward movement until it reaches the position shown in Fig. l.

The pressures in pressure chamber I4 and sealing chamber I5 may be controlled in any desirable manner and, in the apparatus of Fig. 1, have been shown as controlled by an electrically operated control valve mechanism generally indicated at 58. This control valve mechanism 58 includes a control valve casting 5I'that is suitably secured to the upper casting I2, there preferably being a sealing gasket 52 interposed between the control valve casting 5| and the upper casting I2. The control valve casting 5| is provided with a control chamber 53 that is connected to the sealing chamber I5 by means of passages 54 and 55 which are respectively formed in the control valve casting 5| and the upper casting \I2. The control chamber 53 is further placed in com-v munication with the pressure chamber I4 by means of passages 56 and 51 which are respectively formed in the control valve casting 5| and the upper andlower castings I2 and II. The

' control chamber 53 also is arranged to communicate with the exterior of control valve casting 5| by means of a passage 58 formed therein. Communication between passages 58 and either passage 54 or passage 56 is controlled by a valve head 59 that is secured to an upwardly extending valve stem 68. 8

The control valve casting 5| is provided with an upwardlyextendingmylindrical extension 8| that is exteriorly screw-threaded and receives a casting B2 of substantially circular formation. This casting 62 receives a circular spring washer 64 which is. held in place by a spring clip 65. The casting 62 also supports an upwardly extending nonmagnetic, but electrically conductive, tubular shell 66 that has its upper end closed off by a non-magnetic but conductive plug 61. Surrounding the tubular shell "66 is a first magnetic steel disc 68, an electromagnetic coil 69 and a second magnetic steel disc 18. A cylindrical housing 1I surrounds the discs 58 and 18 and electromagnetic winding 89 and rests upon the casting 62. An upper casting 12 is held in engagement with the upper edge of cylindrical housing H by means of a nut 13 which cooperates with a magnetic screw 14 that extends upwardly through the plug 61. A coiled spring 15 is preferably interposed between the under surface of casting 12 As a result, if the,

and the upper surface of disc 18 to press the disc 18, electromagnetic winding 59 and the disc 68 against the casting 62.

Located within the tubular shell 66 is an armature or plunger 88 that is provided with an in-' ternal bore which is closed off by a threaded plug 8|. The valve stem 68 extends through the plug 8| and terminates within the plunger formed by the bore in plunger 88 and the plug 8|. A collar 82 is threaded upon the terminal end of valve stem 88 and a coiled spring 83 is interposed between the collar 82 and the plug 8| whereby the collar 82 is normally held against the plunger 88. The electromagnetic winding 69 is provided with lead wires 84.

When the electromagnetic coil 69 is deenergized, the valve head 59 is in the position shown in Fig. l of the drawings wherein pressure chamber I4 and sealing chamber I5 are placed in communication with each other by means of passages 51 and 58, control chamber 53 and passages 54 and 55. The pressures in pressure chamber I4 and sealing chamber I5 are therefore equal. If the electromagnetic coil 89 be energized however, the plunger 88 moves upwardly and moves valve head 59 upwardly to close 01f communicationbetween passage 54 and passage 58 and to establish communication between passage 54 and passage 58. The pressure in sealing chamber I5 can thereby drain off through passages 55 and 54, control chamber 53 and passage 58, so that the pressure chamber I4 may be subjected to a higher pressure than is present in the sealing chamber I5. In this manner, if the pressure chamber'M-is subjected to a source of pressure, deenergization of electromagnetic coil 89 causes such pressure to be applied both to the pressure chamber I4 and the sealing chamber I5. Energization of electromagnetic winding 69, however, prevents the flow of fluid from the pressure chamber I4 and operates to exhaust the sealing chamber I5 whereby the diaphragm I3 moves upwardly to lift valve disc 33 from valve seat 32.

A manually operable valve 85 is preferably provided to enable lifting of the diaphragm under manual control. If the manually operable valve 85 is turned a quarter revolution in counter-clockwise direction, as viewed in Fig. 1, then the passage 51 is closed off and the sealing chamber I5 placed in communication with exhaust pipe I88 irrespective of the position ofvalve head 59. Under these conditions, the diaphragm I3 will be raised regardless of the. position of valve head 59.

For further details of the construction and operation of the control valve 58, reference maybe had to the copendingapplication of Willis H. Gille, Ser. No. 740,574, filed August 20, 1934.

In manyinstances, it is desired that a motor, such as the pressure motor I8 operate a second or auxiliary control device in addition to the first control device, such as the main fuel valve shown herein. For this purpose, a shaft 98 extends through a bushing 88 threaded into the upper casting I2 so that one of its ends terminates outside of casting I2 and its other end terminates within the sealing chamber I5. This shaft 98 is provided with an enlarged portion 9|, there being a conical portion 92 which joins the enlarged portion 9| and the main shaft 98. This conical portion 92 is arranged to engage a conical depression formed in the bushing85, being placed into such engagement by means of coiled spring 93. One end of this coiled spring 93 abuts an opcrating lever 94 that is secured to shaft 98, as

by a set screw 95, and the other end preferably extends into a depression 96 formed in the upper casting I2. This operating lever 94 terminates centrally in the sealing chamber I5 and is pivoted to a bracket 91 which in turn is secured to a counter-weight 98. A stop member 99 is preferably secured to the lower'portion of counterweight 98. The counter-weight 98 normally biases the operating lever 94 to the position shown in Fig. 1 wherein the stop member 99 engages the upper counter-weight but it will 2.: noted thatlthere is no direct connection between the operating lever 94 and the diaphragm I3.

Turning now to Fig. 3, the apparatus of the present invention is shown applied to a gas-fired heater I00. The inlet ll of valve casing I6 is connected to a gas supply pipe IM and the outlet of valve casing I6 is connected to a pipe I02. The pipe I02 extends through a secondary air housing I03 or usual construction and connects with the burner (not shown) located within heater I00. The secondary air housing I03 is provided with the usual secondary air damper I04 which is connected to shaft 90 by means of a secondary air arm I05 and a connecting spring or cable I06. Any suitable automatic control, such as a room thermostat, is indicated at I01 and is connected to the lead wires 84 of electromagnetic winding 69. The passage 58 is connected to a pipe I08 by which gas exhausted from the sealing chamber I5 may be conducted to any desired point of disposal. In this particular illustration, the pipe I08 is shown leading to the interior of heater I00 so that the exhausted gas may be consumed therein or otherwise disposed of. Pressure from the gas supply line IOI may be transmitted to the pressure chamber I4 by any desirable arrangement and is herein shown as being transmitted thereto by the provision of an opening I09 which extends through the circular disc 2I and bracket I9.

With the control device or room thermostat I0I satisfied so that the electromagnetic winding 69 is deenergized, the pressure chamber I4 and the sealing chamber I5 are in communication with each other as heretofore described so that line pressure flows from the valve casing I6 through opening I09 to pressure chamber I4, through passages 51 and 56 to control chamber 53, and through passages 54 and 55 to the sealing chamber I5. The pressure chamber I4 and sealing chamber I5 are therefore placed under equal pressure so that diaphragm I3 and valve disc 33 assume the position shown in Fig. 1. The operating lever 94 sh-auld also be in the position shown in Fig. 1 by reason of its counter-weight 98 and under these conditions secondary air damper I04 is closed. If the room thermostat I01 now calls for heat and energizes the electromagnetic winding 69, the passage 56 will be closed off by raising of valve head 59 as previously described thereby preventing flow of fluid from the pressure chamber I4. Such action also connects the sealing chamber I4 to pipe I08 so that the gas in sealing chamber I5 is exhausted to the heater I00. The pressure in pressure chamber I4 is thereby made larger than the pressure in sealing chamber I5 whereupon diaphragm I3 moves upwardly. Initial upwardmovement of diaphragm I3 causes clockwise rotation of shaft 9| so that the right end of secondary air arm I05 moves downwardly and begins to open secondary air damper I04. When diaphragm I3 has moved upwardly sufficiently to take up the lost motion between washer and pin 44, the continued upward movement of diaphragm I3 not only opens secondary air damper I04 more widely but also lifts valve disc 33 from engagement with valve seat 32.- In this manner, upon a call for heat, the secondary air damper and main fuel valve are both opened, it being noted that the secondary air damper is partially opened before the main fuel valve begins to open. The fuel thus issuing to heater I00 may be ignited in any of the manners well known in the art and the heater I00 in turn serves to raise the temperature of the space in which the main control or room thermostat IN is located. When the room thermostat I01 becomes satisfied and deenergizes.electromagnetic winding 69, the valve head 59 returns to the position shown in Fig. 1 so that sealing chamber I5 is no longer connected to the pipe I 08 but is again placed in communication with pressure chamber I4. The pressures in pressure chamber I4 and sealing chamber I5 will thereby be equalized and the diaphragm I3 will begin moving downwardly under the biasing force of counterweights 40, 4| and 46. When the diaphragm I3 has moved downwardly sufliciently, valve disc 33 will again engage valve seat 32 but continued downward movement of diaphragm I3 will be permitted by reason of the lost motion connection between valve stem 34 and bracket 43. During this downward movement of diaphragm I3, the counterweight 98 should cause counterclockwise rotation of shaft 90 with a consequent raising of the right hand end of secondary air arm I05 to close the secondary air damper I04. But if any of these parts should stick so that the shaft 9I does not return to the position shown in Fig. 1, it will be evident that the diaphragm I3 can move downwardly to close the main fuel valve nevertheless, since the operating lever 94 only has a one way connection with the diaphragm I3. During this closing movement, of course, the valve disc 33 will seat upon valve seat 32 before the secondary air damper I04 is completely closed.

If it should be desired to manually open the main fuel valve, this can be accomplished by operating manual valve 85 in the manner heretofore set out.

If the diaphragm I3 should become ruptured so that gas fiows from the pressure chamber directly to the sealing chamber I5, then the pressure in such chambers will be equalized, irrespective of the position of manual valve 85 or the valve head 59. In the event the valve head 59 is raised during such time, the pressure in pressure chamber I 4 and sealing chamber I 5 will tend to exhaust through the pipe I08 but the valve disc 33 will remain in engagement with the valve seat 32 or will move into engagement'therewith since the pressures in pressure chamber I4 and the sealing chamber I5 are equal, it being remembered that the diaphragm I3 is biased to its lowermost position by counter-weights 40 and 4|" and the valve disc 33 is additionally biased to closed position by the counter-weight 46.

Turning now to Fig. 4, an improved and modified form of the invention is disclosed. Here again, the motor means is illustrated as a pressure motor, generally indicated at IIO, although motors of other types could well be used as to certain phases of the invention. This pressure motor H0 is comprised by a lower casting III and an upper casting I I 2 which seal a diaphragm II3 therebetween. The lower casting III and the diaphragm II3 form a pressure chamber II4 of which the diaphragm II3 constitutes a-movable wall. Similarly, the upper casting H2 and. the diaphragm H3 form a sealing chamber H5 of which the diaphragm H3 also constitutes a movable wall.

The diaphragm H3 controls a valve mechanism that includes a valve casing II6 which is provided with the usual inlet port I I1 and the usual outlet port H8.

A bracket H9 is secured to the lower casting III as by means of screws I20, there being a sealing diaphragm I2I interposed between the bracket H9 and the lower casting III. The lower casting III is provided with an opening I22 which is sealed off by this sealing diaphragm I2 I A collar I23 is provided with a flange I24 that overlies the edge of a circular disc I25 which is secured to the bracket I I9 by any suitable means such as the rivets I26. The collar I23 is-threaded upon a cylindrical extension I21 of the valve casing H6 whereby the valve casing H6 is securely clamped to the disc I in a fluid tight manner.

The valve casing I I6 is provided with the usual partition wall I28 that is provided with a valve opening I29 which in turn defines a valve seat I30. A valve disc I3I cooperates with the valve seat I30 to prevent or permit communication between the inlet I I1 and the outlet I I8. The valve disc I3I is carried by a valve stem I32. The valve stem I32 extends upwardly through a guide or bushing I33 which is secured to bracket H9 and extends downwardly through the disc I25. Loosely mounted upon the valve stem I32 and located Within the chamber formed by bracket H9 and the sealing diaphragm I2I is a counter-weight I34, the limit of downward motion of which upon the valve stem I32 is limited by a pin I35 which extends through the valve stem I32. The valve stem I32 is sealed to the sealing diaphragm I2I- by nuts I36 which are threaded upon the valve stem I32 and engage opposite sides of diaphragm A pair of counter-weights I40 and MI are secured respectively to the upper and lower surfaces of diaphragm H3 and substantially centrally thereof as by means of rivets I42. A bracket I43 is also secured to the underside of diaphragm H3 and preferably by these same rivets I42. A pin I44 extends through the upper end of valve stem I32 and is adapted to be engaged by a washer I45, upon upward movement of bracket I43 whereby a lost motion connection is provided between the diaphragm H3 and the valve stem I32.

In this embodiment of the invention, the pressures in pressure chamber H4 and in sealing chamber H5 are shown controlled by two control valve mechanisms generally indicated at I and I5I. The control valve mechanism I 50 includes a casting I52 that may conveniently correspond in general outline to the casting 5i of the apparatus of Fig. 1 and is supported by and secured to the upper casting H2, there being a sealing gasket I53 interposed therebetween. Casting I52 is provided with a control chamber I54 which communicates with the pressure chamber H4 by means of passages I55 and I56. The control chamber I54 also communicates with a passage I51 which leads to the exterior of casting I52 and may be conveniently connected to an exhausting pipe I50. A valve head I59, which is located in the control chamber I54, serves selectively to close off the passage I51 or the passage I55. The control casting I52 further is provided with a passage, I that directly connects .sage I51 to exhaust pipe I58.

the control chamber I54 with the exterior of the casting I52 and is provided with a passage I6I that connects the exterior of casting I 52 with the passage I55. The valve head I59 is secured to a valve stem I62 which corresponds to the valve stem 60 of the apparatus of Fig. 1 and it will be understood that the electromagnetic means for operating the valve stem 60 of the mechanism of Fig. 1 may conveniently be used as the operating mechanism for the valve stem I62 of the apparatus of Fig. 4.

The control valve I5I includes a casting I10 that is provided with a control chamber "I. This control chamber I1I communicates with passages I12, I13 and I14 which lead to the exterior walls of casting I10. The passage I14 continuously communicates with the control chamber I1I but the passages I12 and I13 are placed selectively into communication with the control chamber "I by means of a valve head I15 that may be controlled by a ,valve stem I16.

The pressure chamber I I4 may be subjected to any source of fluid pressure in any desired manner and is herein shown as connected to the inlet side of valve casing H6 by means of a pipe I80. The sealing chamber H5 communicates with the passage I14 and therefore with the control chamber I1I of control valve I5I by means of a pipe IOI. The passage I60 of control valve I50 is connected to the passage I13 of control valve I5I by a pipe I82. The passage I6I of control valve I50 is connected to passage I12 of control valve I5I by a pipe I83.

With the parts in the position shown, pressure chamber H4 is connected'to sealing chamber H5 so that the pressures therein are equal. It will be noted that pressure from the inlet of valve casing H6 is transmitted to pressure chamber H4 by pipe I80 and from pressure chamber H4 to scaling chamber H5 by means of passages I56 and I55, control chamber I54, passage I60, pipe I82, passage I13, control chamber I1I, passage I14, and pipe I8I. Since the pressures in pressure chamber H4 and sealing chamber H5 are equal, the diaphragm H3 has moved downwardly to the position shown in Fig. 4 of the drawings under the influence of counter-weights I40 and MI and the valve disc I3I is engaged with the valve seat I30 under the influence of counterweight I34. If the valve head I59 is now moved upwardly in response to a change in some condition, such as a call for heat by aroom thermostat as shown in the system of Fig. 3, passage I55 will be closed off so that fluid can no longer fiow from the pressure chamber H4. Also, sealing chamber H5 will be placed in communication with exhaust pipe I58 by means of pipe IOI, passage I14, control chamber I1I, passage 13, pipe- I 82, passage I60, control chamber I54, and pas- Pressure is no longer permitted to drain from pressure chamber H4 and sealing chamber H5 is exhausted. As

a result, the pressure in pressure chamber H4 becomes greater than the pressure in sealing chamber H5 so that diaphragm H3 is moved upwardly. After the lost motion between bracket I43 and pin I44 has been taken up, continued upward movement of diaphragm H3 serves to raise valve disc I3I from valve seat I30 whereupon communication is established between inlet H1 and outlet H8. If, while valve head I59 is raised so as to prevent the flow of fluid from pressure chamber I I4 and to connect sealing chamber H5 to exhaust pipe I58, valve head I15 is raised, the pressure chamber H4 and sealing chamber H5 arc-nasaare again placed in communication with'each other and exhausting from sealing chamber I II is prevented. Pressure chamber II4 under these conditions is connected to sealing chamber II5 by passages I56 and I6I, pipe I83, passage I12, control chamber I1I, passage I14 and pipe I8I. Fluid can no longer flow to the exhaust pipe I58 from sealing chamber II5 by way of pipe I82 since the passage I13 is now closed 011 by valve head I15. With the pressures again equalized in pressure chamber 4 and sealing chamber 5, the diaphragm II3 will move downwardly 7 under the influence of counter-weights I40, I

and I34. This downward movement will first result in seating of valve disc I3I upon valve seat I30. Thereafter, continued downward movement of diaphragm I I3 will continue by means of counterweights I and MI, the lost motion connection between valve stem I32 and bracket I43 permitting such continued downward movement of diaphragm 3 after valve disc I3I seats upon valve seat I30.

If valve head I59 now returns to the position shown in Fig. 4 of the drawings but'valve head I15 remains in its raised position, the pressures in pressure chamber I I4 and sealing chamber I I5 will remain equal and the parts will remain in the position shown in Fig. 4.

The valve head I59, as previously pointed out, may conveniently be controlled by room temperature conditions and the valve head I15 may conveniently be controlled by heater conditions and thereby operates as a high limit control to prevent opening of the main valve in the event the heater condition which controls the valve head I15 becomes excessive.

The control valve I50 additionally includes a. manually operable valve I85 which is arranged to close off the passage I55 upon manual manipulation whereby to prevent the flow of fluid from the pressure chamber I I4. Such manual manipulation of valve I85 also serves to connect passages I60 and I51. As a result, sealing chamber H5 is connected to exhaust pipe I58 through pipe I8I, passage I14, control chamber I1I, passage I13, pipe I82, and passage I60 if the valve head I15 be in its lowermost position, due to a failure in electrical power or the like. But if the manual valve I85 is so manipulated when the valve I15 is in its upper position because of excessive heater conditions or the like, the sealing chamber 5 is connected to pressure chamber I I4 by means of pipe I8I, passage I14, control chamber I1l, passage I12, pipe I83, passage I6I and passage I56. By this arrangement, provision is made for manually causing opening of the main valve irrespective of the operation of valve head I59 but the arrangement further is such that the main valve cannot be opened if the valve head I15 is in a position indicating that the main valve should be closed. I

In the apparatus of Fig. 4, the'diaphragm H3 is also utilized to operate control devices other than the main valve. .In order to accomplish this, an operating lever I90 is secured to a shaft I9I, as by the screw and nut arrangement I92,

the shaft I9I extending exteriorly of the upper natessubstantiallycentrally of the diaphragm I13 and carries a roller I93 which is adapted to 'be' engaged by the counterweight I40 upon upward movement of the diaphragm II3. A lever I94, which is located exteriorly of the casing II2, has one of its ends secured to the shaft 'I9I and carries a roller I95 at its other end. This lever I94 is connected to a secondary air damper arm I96 by a link I91, the secondary air damper arm I96 being pivoted to a bracket I98. A counterweight I99 is adjustably mounted upon the secondary air damper arm I96 and operates to bias the operating lever I90 to the position shown.

The lever I94 in addition to operating the secondary air damper arm I96 also preferably operates an expanding or flare pilot. A flare pilot casting 200 is secured to the lower casting I I I, there preferably being a bracket MI and suitable sealing gaskets 202 interposed between the lower in the art.

Communication between inlet chamber 203 and outlet-chamber 205 is controlled by a pilot valve 201 that is secured to a valve stem 208. The casting 200 screw-threadedly receives a plug 209 which in turn screw-threadedly receives an adjustable stop member 2l0 which may be adjusted to maintain the pilot valve 201 in a predetermined minimum open position. The pilot valve 201 is biased towards closed position and into engagement with the adjustable stop 2I0 by means of a coiled spring 2I I. Suitable packing 2I2 is placed about valve stem 208. A coiled spring 2I3 has one of its ends abutting the packing 2I2 and its other end abutting an abutment 2I4 that is threaded into the stop member 2l0.

The bracket 20l supports a pilot operating lever 2I5 in pivotal fashion as indicated at 2I6. This lever 2 I5 is provided with an adjustable screw 2 I1 that is adapted to engage the valve stem 208. The lever 2| 5 is further provided with an upper semi-circular cam surface 2I8 and a lower semicircular cam surface 2I9 which are adapted to cooperate with the roller I95 in a manner to be explained hereinafter.

The operation of the complete apparatus of Fig. 4 will now be explained. With the parts in the position shown, this pilot valve 201 is open a minimum amount as determined by the stop 2I0 so that a constant minimum supply of gas is flowing to the pilot pipe 206. The main valve is closed and the secondary air arm I96 is in position to close the secondary air damper. Now if the valve head I59 is raised as heretofore described, the diaphragm I I3 will begin moving upwardly. Initial upward movement of diaphragm 3 causes clockwise rotation of shaft I9l whereupon the right hand ends of levers I94 and I96 start moving downwardly. Such downward movement of the right end of lever I96 begins opening the secondary air damper. Downward movement of the right end of lever I 94 causes the roller I95 to begin moving out of the semi-circular cam portion 2I8 and towards the semi-circular cam surface 2I9.

As a result, thescrew 2I1 moves to the left thereby from the seat I 30. Gas therefore flows to the main burner and is ignited by the expanded pilot. As the upward motionof diaphraghm II3 continues, roller I95 moves into the semi-circular cam surface 2l9 whereupon spring 2 returns the pilot valve 201 and lever 2I5 to the position shown in Fig. 4. The pilot is now again contracted, the secondary air damper is completely open and the main valve is completely open. Now if the valve head I59 returns to-the position shown, or if the valve head I15 is moved to its upper position, the pressures in pressure chamber Ill and sealing chamber II are again equalized as heretofore explained. Diaphragm H3 begins moving downwardly and valve disc I3I immediately moves towards closed position. After the valve disc I3I has completely seated upon the seat I36, the diaphragm II3 continues its downward motion until it reaches the position shown in Fig. 4. During this downward motion of diaphragm II3, the operating'lever I90 should follow the same due to the biasing action of counterweight I99. Such downward movement of operating lever I90 results in closing secondary air damper and moves the roller I95 from the cam surface 2I9 to the cam surface 2I8 so that the pilot valve 201 is again momentarily opened wide- 1y during the shut-down operation. But if the pilot valve or the secondary air damper or any of the interconnecting mechanism should stick and thereby prevent the operating lever I90 from following the downward movement of diaphragm -II3, then diaphragm II3 can nevertheless move downwardly because of the one way connection between it and the operating lever I90.

The casting I52 of control valve I50 is shown provided with a passage 225 and upper casting H2 is shown as provided with a passage 226. However, communication between these passages is prevented by the gasket I53. However, if it be desired to omit the control valve I5I, then a different gasket I53 having an opening therein to provide communication between passages 225 and 226 can be substituted or the gasket I53 may be arranged so that turning it to a diiferent position establishes such communication. The pipes I82 and I83 under these conditions would be removed and the passages I60 and- I6I plugged. Then when the valve head I59 is in the lower position shown, pressure chamber I I4 would communicate with sealing chamber H5 in the same manner asdisclosed in Fig. 1 and upward movement of valve head I59 would prevent the flow of fluid from pressure chamber IM and connect the sealingchamber II5 to theexhaust pipe I58 in the same manner as disclosed in Fig. 1. In this manner, the apparatus of Fig. 4 may be interchangeably used either with or without an auxiliary control valve such as a limit control valve.

With the apparatus of Fig. 4, irrespective of whether it be used with a single control valve or two control valves, rupture of diaphragm II3 will cause an equalization of pressures in the pressure chamber H4 and sealing chamber 5 so that the diaphragm II3 moves to its lowermost ment of the lever I 90 in a downward direction I so as to follow the downward movement of the diaphragm H3.

It will be noted that the apparatus of the present invention provides an arrangement in which a single motor positively operates a first control device such as a main gas valve and is additionally arranged to operate a second control device such as a secondary air damper to one position, the arrangement being such that if a second control device fails to return from such position, the motor means can nevertheless operate the first control device or main valve. This positively provides for closing of the main valve when it should be closed even though the auxiliary apparatus controlled by the same motor fails to return to its original position because of sticking or for some other reason. It will be further noted that this operation of the second control device is obtained by having an operator extend into the path of movement of the motor which in this case is a movable wall or diaphragm. The present invention also provides an arrangement in which either a secondary air damper or a flare pilot, or both, are operated at least partially, prior to opening of the main valve. The present invention also contains many other novel features which will now be apparent.

It will be readily appreciated that many changes can be made in the specific embodiments herein disclosed without departing from the spirit of the present invention and we therefore intend to be limited only by the scope of the appended claims.

We claim:

1. In combination, a burner, a fuel valve in control of the flow of fuel to said burner, a pair of pressure chambers defined by a movable wall, connections between said movable wall and fuel valve, the movable wall and fuel valve normally tending to assume a given position, a first control valve and connections operative selectively to. subject both of said pressure chambers to the fuel pressure or to exhaust a first of said chambers while maintaining the second of said chambers subject to the fuel pressure whereby said movable wall and fuel valve are either permitted to move to said given position or are forcibly moved therefrom, a second control valve selectively operable to permit such control by said first control valve or to subject both of said pressure chambers to the fuel pressure irrespective of the position of said first control valve whereby the movable wall and fuel valve move. to said given position, and a third control valve operable to subject the second of said chambers to fuel pressure while exhausting said first chamber irrespective of the position of said first control valve.

2. In combination, a burner, a valve in control of the supply of fuel to the burner, an air damper in control of the supply of air to the burner, a flare pilot valve, a pressure motor having a wall movable to first and secondpositions, connections between .said movable wall, fuel valve, air

, damper, and flare pilot valve operable to open the fuel valve and air damper and momentarily to open'said flare pilot valve upon movement of the wall from said first position to said second position, and means in control of said motor.

' 3. In combination, a burner, a fuel valve in control of the flow of fuel to the burner, a flare pilot valve, a pressure motor having a wall movable from a first position to a second position, a direct connection between said flare pilot valve and movable wall operable to open said flare pilot valve upon initial movement of said movable wall from said first position to said second position, a lost motion connection between said movable wall and fuel valve operative to open the fuel valve only after the flare pilot valve has been opened when the movable wall is so moved, and means in control of said pressure motor.

4. In combination, a burner, afuel valve in control of the flow of fuel to the burner, a flare pilot valve, a pressure motor including a movable wall, a direct connection between said movable wall and said flare pilot, and a lost-motion connection between said movable wall and said fuel valve.

5. In combination, a burner, a fuel valve in control of the burner, a pressure motor including a movable wall, a connection between said'movable wall and fuel valve, an operator extending into the path of movement of said movable wall and engageable thereby when moving in valve opening direction, an air damper connected to said operator, a flare pilot valve, and connections between said operator and flare pilot valve, the one-way connection thus produced between said movable wall and air damper and flare pilot permitting movement of said movable wall to fuel valve closed position irrespective of movement of said air damper.

6. In combination, a burner, a fuel valve in control of the flow of fuel to said burner, a pressure motor including a movable wall, an operator normally engaged with the movable wall and movable thereby in only one direction, an air damper arm and a flare pilot valve connected to said operator for operation thereby when so moved, and a lost-motion connection between said movable wall and fuel valve.

7. In combination, a pressure motor, a fuel valve controlled thereby, an operator also controlled by the pressure motor, a pilot valve, and connections between the operator and pilot valve including cam means operative to momentarily flash said pilot upon movement of said operator in a single direction. I

8. In combination, a pressure motor including a movable wall, a fuel valve, connections between said movable wall and fuel valve for operating the same, an operator extending into the path of movement of said movable wall when moving in fuel valve opening direction, a pilotvalve, connections between said pilot valve and operator to open said pilot valve when the movable wall moves in fuel valve opening direction, and control means to vary the pressure to which said movable wall is subjected.

9. In combination, a pressure motor including amovable wall, a fuel valve, a lost-motion connection between said fuel valve and movable wall, an operator extending into the path of movement of said movable wall when moving in fuel valve opening position and arranged to be moved thereby upon initial movement of the movable wall in fuel valve opening direction, a pilot valve controlled by said operator, and con trol means to vary the pressure to which said movable wall is subjected.

10. In combination, a burner, a fuel valve in control of the flow of fuel to the burner, a flare pilot valve, a pressure motor having a movable wall actuated by changes in the relative pressure on opposite sides of said wall, a lost motion connection between said valve and said diaphragm and a direct connection between said diaphragm and said fiare pilot valve such that upon movement of said movable wall in one direction, said flare pilot valve is first opened to its full open position and upon further movement of the wall, said fuel valve is moved to open position, and control means operative upon a decrease in temperature of a space heated by said burner, to vary the relative pressure on opposite sides of said diaphragm so as to cause said diaphragm to move upwardly to first fully open the pilot valve and to then open said fuel valve.

FREDERICK S. DENISON. CARL G. KRONMILLER. 

